EP1830067B1 - Kompressor der spiralbauart - Google Patents

Kompressor der spiralbauart Download PDF

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Publication number
EP1830067B1
EP1830067B1 EP04807594.9A EP04807594A EP1830067B1 EP 1830067 B1 EP1830067 B1 EP 1830067B1 EP 04807594 A EP04807594 A EP 04807594A EP 1830067 B1 EP1830067 B1 EP 1830067B1
Authority
EP
European Patent Office
Prior art keywords
scroll
main shaft
closed container
compression
orbiting
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Fee Related
Application number
EP04807594.9A
Other languages
English (en)
French (fr)
Other versions
EP1830067A1 (de
EP1830067A4 (de
Inventor
Kenji Yano
Toshiyuki Nakamura
Masaaki Sugawa
Kunio Tojo
Fumihiko Ishizono
Masayuki Kakuda
Shin Sekiya
Masahiro Sugihara
Toshihide Koda
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Mitsubishi Electric Corp
Original Assignee
Mitsubishi Electric Corp
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Mitsubishi Electric Corp filed Critical Mitsubishi Electric Corp
Priority to EP16176715.7A priority Critical patent/EP3096017B1/de
Publication of EP1830067A1 publication Critical patent/EP1830067A1/de
Publication of EP1830067A4 publication Critical patent/EP1830067A4/de
Application granted granted Critical
Publication of EP1830067B1 publication Critical patent/EP1830067B1/de
Expired - Fee Related legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/02—Lubrication; Lubricant separation
    • F04C29/023—Lubricant distribution through a hollow driving shaft
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • F04C18/0207—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
    • F04C18/0215—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form where only one member is moving
    • F04C18/0223—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form where only one member is moving with symmetrical double wraps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • F04C18/0207—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
    • F04C18/0246—Details concerning the involute wraps or their base, e.g. geometry
    • F04C18/0253—Details concerning the base
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
    • F04C23/008—Hermetic pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/02—Lubrication; Lubricant separation
    • F04C29/028—Means for improving or restricting lubricant flow
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/12—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2240/00—Components
    • F04C2240/80—Other components
    • F04C2240/806—Pipes for fluids; Fittings therefor

Definitions

  • the present invention relates to a scroll compressor, and more particularly to a scroll compressor having volute teeth on both surfaces of a base plate of an orbiting scroll.
  • a compression section is disposed in an upper space in a container, a motor for driving is placed in a lower space, and a lubricating oil storage chamber is formed below the motor.
  • the compression section is formed by combination of an orbiting scroll having an volute tooth formed on only an upper surface of an orbiting scroll base plate, and a fixed scroll opposed to the above volute tooth.
  • a compression chamber is formed by driving the motor via an eccentric shaft connected to a lower surface of the orbiting scroll (for example, refer to Patent Document 1).
  • volute teeth are formed on both surfaces of an orbiting scroll base plate
  • compression chambers are formed on an upper and a lower surfaces of the orbiting scroll by opposing fixed scrolls to the respective volute teeth
  • the orbiting scroll is driven by a shaft penetrating through each of the scrolls.
  • the heights of the volute teeth, which are formed on the upper and the lower surfaces of the orbiting scroll are made different, and an upper compression chamber and a lower compression chamber are connected in series relationship to perform two-stage compression (for example, refer to Patent Document 2).
  • JPH08326671A discloses a compressor to secure lubrication to each bearing part and slidably moving part by arranging an oil feed passage communicating with a lubricant sump, an oil feed passage eccentric to the axial center of the first oil feed passage, and a bearing oil feed hole oriented radially outward.
  • JPH08165993A discloses a compressor to improve machine efficiency through improvement of constitution to balance a rotation system and to improve reliability through endurance of oil return, in a shaft-through type double-tooth scroll fluid device.
  • JPH08170592A discloses a compressor to enable compression with high efficiency in a small-sized compressor, and to reduce the thrust force applied to a swivel scroll end plate from high pressure stage to low pressure stage.
  • the conventional scroll compressors are constructed as described above.
  • the compression section is placed in the upper space while the motor is placed in the lower space, so that it is necessary to pass a lead wire connected to the motor through the compression section to lead it to the upper space and connect it to a terminal in the case where the terminal is provided above, and therefore, there is the problem of unfavorable operability.
  • bearing structure is provided only at the lower position of the compression section, so that there are the problems of one-side abutment of the bearing due to tilt of the shaft, and an increase in associated bearing loss and burning. Further in case the orbiting scroll has the volute tooth only on one side, thrust load occurs due to compression of the operating gas, and therefore, there is the problem of needing a thrust bearing.
  • Patent Document 2 the compression chambers are formed on both sides of the orbiting scroll, thrust loads by the compression of the operation gas are cancelled out, and as a result, the load of the thrust bearing is reduced.
  • there are some problems of complicating the construction of the scroll because it is necessary to control the ratio of the height of the volute tooth on the upper surface of the orbiting scroll and the height of the volute tooth on the lower surface so that the minimum closed volume of one compression chamber and the maximum closed volume of the other compression chamber are substantially equal, or to be substantially equal to the ratio of the maximum closed volume and the minimum closed volume of one compression chamber.
  • the present invention is made to overcome the above described problems, and has an object to provide a scroll compressor that has favorable assembling property, does not require a thrust bearing, has a compression section supported by bearing structure on both sides and is simple in a structure of a scroll.
  • the present invention encompasses a scroll compressor comprising a compression section provided in a closed container, said closed container being vertically disposed, said compression section being disposed at a lower portion in said closed container and said compression section including an orbiting scroll having volute teeth formed substantially symmetrically on both surfaces of an orbiting base plate, and a main shaft being penetrated through and fixed at a center portion of said orbiting scroll and pair of fixed scrolls opposed to said both surfaces of said orbiting scroll, each of said fixed scrolls having a volute tooth corresponding to each of said volute teeth of said orbiting scroll to respectively form compression chambers, a motor provided in said closed container for driving said main shaft, said motor being disposed at an upper portion in said closed container, a suction pipe provided to said closed container for introducing a suction gas into said closed container and for causing said suction gas to be sucked into said compression section after cooling said motor, a discharge pipe provided to said closed container for discharging said suction gas compressed by said compression section, a lubricating oil storage chamber being formed in said
  • the scroll compressor according to this invention is constructed as described above. Accordingly in case of assembling a vertical type, for example, the compression section is placed in a lower space of the container, the motor is placed in an upper space, and a glass terminal can be provided at an upper end portion above the motor. Therefore, after the compression section and the motor are all fixed inside the container, a lead wire can be finally connected to the terminal, and therefore, assembling property is improved.
  • substantially symmetrical volute teeth are formed on both surfaces of the orbiting scroll and the thrust loads caused by compression of an operating gas are cancelled by each other so that a thrust bearing does not have to be provided.
  • volute teeth on both surfaces of the orbiting scroll are formed to be substantially symmetrical and have substantially the same heights, and therefore, they are simple in structure and can be formed easily.
  • Figure 1 is a schematic sectional view showing one example of an entire construction using a vertical container according to the first embodiment
  • Figure 2 shows a construction of an orbiting scroll in the first embodiment
  • (a) is a sectional view taken along the line A-A in (c) that will be described later, and the left side shows an upper surface while the right side shows a lower surface
  • (b) is a plane view showing a construction of the upper surface of the orbiting scroll
  • (c) is a plane view showing a construction of the lower surface of the same.
  • Figure 3 shows a construction of a core part located in a center portion of the orbiting scroll shown in Figure 2
  • (a) is a perspective view showing the shape of the core part
  • (b) is a perspective view showing a construction of a seal ring each provided at an upper surface and a lower surface of the core part
  • Figure 4 is an explanatory sectional view for explaining an operational effect of the seal ring in the core part
  • Figure 5 shows the construction of a lower side fixed scroll in Figure 1 in the first embodiment
  • (a) is a plane view
  • (b) is a sectional view taken along the line A-A in (a).
  • a motor 2 is placed at an upper portion in a vertical closed container 1, a compression section 3 is placed in a lower portion, and a lubricating oil storage chamber 4 is formed under the compression section 3.
  • a suction pipe 5 is provided for sucking a suction gas in the closed container 1 at an intermediate portion between the motor 2 and the compression section 3, and a glass terminal 6 is provided at an upper end of the closed container 1 at the upper side of the motor 2.
  • the motor 2 is constructed by a known stator 21 formed into a ring shape, and a rotor 22 supported to be rotatable in the inside of the stator 21.
  • a main shaft 7 is fixed to the rotor 22, and the main shaft 7 penetrates through the compression section 3 to extend to the lubricating oil storage chamber 4. The relationship between the compression section 3 and the main shaft will be described later.
  • the compression section 3 includes an orbiting scroll 31 having volute teeth formed on an upper surface and a lower surface of an orbiting base plate in substantially symmetrical shape with substantially same heights, an upper fixed scroll 33 which is disposed to be opposed to the upper surface of the orbiting scroll 31 and has an volute tooth which corresponds to the upper surface volute tooth of the orbiting scroll 31 to form a compression chamber 32, a lower fixed scroll 34 which is disposed to be opposed to the lower surface of the orbiting scroll 31 and has a volute tooth which corresponds to the lower surface volute tooth of the orbiting scroll 31 to form the compression chamber 32, and a known Oldham joint 35 which is placed between the lower fixed scroll 34 and the orbiting scroll 31.
  • the orbiting scroll 31 has a core part 31A which forms a center portion and is constituted of a curved line such as an arc, and a disk-shaped orbiting base plate 31B which extends on the outer periphery of the core part 31A.
  • a hole 31C, through which a main shaft 7 penetrates, is formed in a center portion, and an orbiting bearing 31D is provided on its inner peripheral wall.
  • a seal ring groove 31E is respectively formed on both surfaces of the core part at an outer side of the orbiting bearing 31D, and a seal ring 31G having an abutment joint 31F as shown in Figure 3(b) is inserted in a respective groove. The details of the seal ring 31G will be described later.
  • a volute tooth is usually formed in an involute curve or an arc outward from its center, and the number of turns of the volute tooth is proportional to the compression ratio of the compressor.
  • the compressor In the case of using an HFC gas in air-conditioning for example, the compressor is operated at the compression ratio of 3, so that the number of turns of the volute tooth needs to be three or more. But in the case of using a CO 2 gas with a low compression ratio, the compressor is operated at the compression ratio of 2, so that the number of turns of volute tooth becomes two or more, and thus it is possible to reduce the number of turns of the volute tooth by one turn as compared with the case of the HFC gas.
  • Two or more turns of a volute tooth are formed respectively on the upper surface and the lower surface of the orbiting base plate 31B in volute curves or arcs substantially symmetrically and substantially in the same height as the core part.
  • substantially symmetrical means that the thickness t, height h, pitch p and the numbers of turns n of the volute tooth shown in Figure 2(a) are substantially equal, and thereby, the reaction force in the thrust direction which occurs at the time of gas compression is made completely or substantially equal.
  • the tooth height of the scroll can be made low, and the volute may be enlarged in the diameter direction into a so-called thin pancake shape, whereby the radial direction force can be made relatively small, and reliability of the journal bearing can be enhanced.
  • volute teeth on the upper surface and the lower surface are made substantially symmetrical, but in actual a slight difference is made to occur in the gas pressures of the upper and lower compression chambers for example in order to give rise a slight thrust force downwardly.
  • a tip seal groove 31H is formed at the upper end surface of the volute tooth as shown in Figures 2(a) and (b) , and a tip seal 36 ( Figure 6 ) is fitted inside of it.
  • an Oldham groove 31J corresponding to the Oldham joint 35 is formed at an outermost peripheral portion.
  • the seal ring 31G provided at the core part 31A is formed as a ring which is rectangular in section as shown in Figure 3(b) and has the abutment joint 31F, and is fitted in the seal ring groove 31E shown in Figure 3(a) .
  • This seal ring 31G is placed in the core part 31A to separate the main shaft 7 and the orbiting bearing 31D from the center side of the volute tooth in order to prevent leakage therebetween, since at the time of a compressing operation, the main shaft 7 and the orbiting bearing 31D are at a low pressure, while the center side of the volute tooth is at a high pressure.
  • the separating action is performed by contact sealing of the seal ring 31G by pressure difference.
  • the seal ring 31G is pressed against the right side wall and to the upper side fixed scroll 33 in the seal ring groove 31E being pressed from the high pressure left side and the lower side as shown by the arrow in Figure 4 .
  • a communication port 31K is formed at the outer side of the seal ring groove 31E.
  • the communication port 31K penetrates through the orbiting base plate 31B in the vertical direction and combines the gases, which are compressed in the compression chambers on both surfaces of the orbiting scroll 31 as will be described later, to flow to a discharge port of the fixed scroll.
  • the communication port 31K is formed as a long hole along the seal ring groove 31E, or is formed as a plurality of holes disposed adjacently each other to perform substantially equivalent action as the long hole, and is provided at the position which is not across the compression chambers, and always communicates with the discharge port of the fixed scroll, that will be described later.
  • Figure 5 shows one example of the lower fixed scroll 34.
  • a hole 34B is formed in a center portion of a fixed base plate 34A through which the main shaft 7 penetrates, and a main shaft bearing 34C is provided on an inner peripheral surface of this hole.
  • a recessed portion 34D is formed in the peripheral portion of the main shaft bearing 34C, i.e. the center portion of the fixed base plate 34A, and accommodates the core part 31A of the orbiting scroll 31 and allows the orbiting movement of the orbiting scroll 31.
  • an volute tooth 34E is formed in two or more turns in the same size as the volute tooth of the orbiting scroll 31 in the volute curve or the arc but is rotated 180 degrees in phase.
  • a discharge port 34F is provided in the recessed portion 34D for discharging the compressed gas without crossing the seal ring 31G of the orbiting scroll.
  • the discharge port 34F is formed as a long hole along an inner side of the innermost volute tooth of the fixed scroll, or is formed as a plurality of holes disposed adjacently each other to perform substantially the equivalent action with the long hole, and is provided at the position which always communicates with the communication port 31K of the orbiting scroll.
  • a discharge passage 34G is formed which communicates with the discharge port 34F and flows the compressed gas out of the compressor via a discharge pipe 8 ( Figure 1 ).
  • a discharge valve 34H is placed at a position opposed to the discharge port 34F in the discharge passage 34G as shown in Figure 1 , and prevents a backflow of the discharge gas.
  • a suction port 34J is provided as a suction inlet of the suction gas to the lower compression chamber.
  • a discharge port 34K ( Figure 1 ) is provided which communicates from the suction port 34J to the lubricating oil storage chamber 4 at the lower portion of the closed container.
  • a check valve 34L is provided for the discharge port 34K at the side of the lubricating oil storage chamber 4 as shown in Figure 1 .
  • the check valve 34L is provided to prevent that oil foams with remaining refrigerant and flows out of the compressor when actuating the compressor.
  • the suction path for suctioning gas into the compression chamber is formed as shown by the broken line arrow G in Figure 1 .
  • the suction path includes the suction port 33A formed in the outermost peripheral portion of the upper fixed scroll 33 and the suction port 34J of the lower fixed scroll 34, and the suction gas is introduced into the respective compression chambers formed both on the upper surface and the lower surface of the orbiting scroll 31.
  • the upper end portion of the main shaft 7 is fitted into the rotor 22 of the motor 2.
  • the main shaft penetrates the through-hole of the upper fixed scroll 33, the through-hole 31C of the orbiting scroll 31 and the through-hole 34B of the lower fixed scroll 34 and is immersed at its lower end portion in the lubricating oil 77 in the lubricating oil storage chamber 4.
  • Figure 6 shows an enlarged view of the penetration structure of the main shaft 7 into the compression section 3 and the structure of the lower end portion of the main shaft 7.
  • a main shaft bearing 33B is provided between the main shaft 7 and the upper fixed scroll 33.
  • a notch part 71 having flat surface, is formed from the portion in contact with the main shaft bearing 33B down to the lower end.
  • a slider 72 having an eccentric hole (not shown) with a partially flat surface corresponding to the notch part 71, is fitted to the notch part 71 of the main shaft 7.
  • the outer peripheral surface of the slide 72 is placed to be in contact with the inner peripheral surface of the orbiting bearing 31D of the orbiting scroll 31 shown in Figure 2 .
  • the slider 72 forming an eccentric shaft in combination with the main shaft, drives the orbiting scroll 31 via the orbiting bearing 31D.
  • recesses 73 are formed for the paths of lubricating oil.
  • an oil feed groove 74 is formed in the vertical direction and allows the recess 73 on the upper surface to communicate with the recess 73 on the lower surface.
  • an eccentric oil feed hole 75 is formed and extended from the lower end to reach the main shaft bearing 33B of the upper fixed scroll 33.
  • An oil feed pump 76 is provided at the lower end of the main shaft 7 and is immersed in lubricating oil 77 at the lower end of the closed container 1.
  • the gas which is sucked into the closed container 1 from the suction pipe 5, flows into a part of the motor 2. After cooling the motor 2, the gas is taken into the compression chambers 32 on the upper and lower surfaces of the orbiting scroll 31 from the suction port 33A provided in the outer peripheral portion of the upper fixed scroll 33 as shown by the broken line arrow G.
  • the orbiting scroll 31 performs orbiting movement, without rotating around its own axis, with respect to the upper and the lower fixed scroll s 33 and 34.
  • a pair of crescent compression chambers which are formed by the known compression principle, reduce their volumes gradually toward the center.
  • the pair of compression chambers finally communicate with each other in the innermost chambers in which the discharge port 34F is present, and flows are guided outside the compressor through the discharge passage 34G.
  • Figure 7 shows the process in which a pair of crescent compression chambers, which are formed by the orbiting movement of the orbiting scroll 31, gradually reduce their volumes toward the center.
  • Figure 7(a) shows the state of the orbiting scroll 31 at the orbit angle of 0°.
  • the diagonally slashed portion represents the volute tooth of the orbiting scroll, and the portion painted in black represents the volute tooth of the fixed scroll.
  • Figure 7(b) shows the state in which the orbiting scroll 31 orbits by the orbit angle of 90° in the counterclockwise direction.
  • a pair of compression chamber A and B moves toward the center while reducing in volume.
  • Figure 7(c) shows the state of the orbit angle of 180°
  • Figure 7(d) shows the state of the orbit angle of 270°.
  • the compression chambers A and B communicate with each other in the innermost chamber in which the discharge port 34F is present, and the gas is discharged from the discharge port 34F.
  • the shape of the core part 31A of the orbiting scroll 31 forms the volute curve up to the portion shown by the broken line, and forms one border of the compression chamber B.
  • the center side from this becomes the curve of the core part and forms the innermost chamber that does not contribute to compression, and forms a border surface in combination with the inner surface of the volute tooth of the fixed scroll 34.
  • the discharge port 34F is provided in the innermost chamber which does not contribute to compression, and is positioned not to cross the aforementioned seal ring 31G during the compression step, so that a sufficient flow passage is ensured.
  • the curve of the core part and the curve of the inner surface of the volute tooth of the fixed scroll are formed to secure a clearance space in order not to block the discharge port 34F completely with the core part 31A during the compression step.
  • compression insufficiency loss occurs in the final discharge step when the operation is performed with a higher compression ratio than a set compression ratio.
  • the compression insufficiency loss means that the pressure in the innermost chamber is higher than the pressure of the compression chambers A and B, when the innermost chamber and the compression chambers A and B communicate each other as in Figure 7(d) for example. Then, backflow occurs to the compression chambers A and B from the innermost chamber, and causes loss of the compression power.
  • the top clearance volume is restrained to a minimum, which is defined as the volume upstream of the discharge valve 34H, namely the total sum of the innermost chamber, the discharge port 34F and the communication port 31K. Further, a little relief portion 34M is formed in the core part 31A. The relief portion 34M is to secure a flow passage by expanding width with reduced radius of the curvature.
  • the lubricating oil passes the flat portion of the notch part 71 formed on the main shaft to flow down and, via the recess 73 formed on the upper surface of the slider 72, flows into the oil feed groove 74 which is formed in the vertical direction on the outer peripheral surface of the slider 72 to lubricate the slider 72.
  • the oil which flowed down in the oil feed groove 74, passes via the recess 73 on the lower surface of the slider, and passes through a return hole 34N formed in the lower fixed scroll 34, and flows towards the center direction of the main shaft, and flows down in the notch part 71 of the main shaft 7 again while feeding oil to the main shaft bearing 34C of the lower fixed scroll 34, and is discharged outside the main shaft from the lower end portion of the main shaft bearing 34C as shown by the arrow, and returns to the lubricating oil storage chamber 4.
  • the oil feed path forms a circulating closed loop from feeding through discharging without directly contacting the flow of the suction gas.
  • the first embodiment is constructed as above, and therefore the compressor is suitable, for example, in a case where a heat exchanger volume of an air conditioner is made large for energy saving, in a case where the apparatus is tuned to perform a normal operation with a low compression ratio as an ice thermal storage system for peak-cut and load-leveling, and in a case where a refrigerant such as a CO 2 gas is used and normal operation is performed at a low compression ratio for air conditioning operation. A high efficiency of the apparatus can be maintained.
  • This invention can be favorably utilized in an air conditioner or an ice heat storage system that are tuned to be normally operated with a low compression ratio, or in an air conditioner using a refrigerant such as a CO 2 gas and having a low compression ratio at normal operation.

Claims (9)

  1. Scrollkompressor, der Folgendes umfasst:
    einen Kompressionsabschnitt (3), der in einem geschlossenen Behälter (1) vorgesehen ist, wobei der geschlossene Behälter (1) vertikal angeordnet ist, wobei der Kompressionsabschnitt (3) an einem unteren Abschnitt in dem geschlossenen Behälter (1) angeordnet ist und der Kompressionsabschnitt Folgendes aufweist:
    • eine orbitierende Spirale (31), die Spiralenmantelzähne hat, die im Wesentlichen symmetrisch auf beiden Oberflächen einer orbitierenden Grundplatte (31B) gebildet sind, und eine Hauptwelle (7), die in die orbitierende Spirale durchgehend eindringt, an deren Mittenabschnitt sie befestigt ist, und
    • ein Paar stationärer Spiralen (33/34), die den beiden Oberflächen der orbitierenden Spirale entgegengesetzt sind, wobei jede der stationären Spiralen einen Spiralenmantelzahn hat, der jedem der Spiralenmantelzähne der orbitierenden Spirale entspricht, um jeweils Kompressionskammern (32) zu bilden,
    einen Motor (2), der in dem geschlossenen Behälter vorgesehen ist, um die Hauptwelle anzutreiben, wobei der Motor (2) an einem oberen Abschnitt in dem geschlossenen Behälter (1) angeordnet ist,
    ein Saugrohr (5), das zu dem geschlossenen Behälter zum Einführen eines Sauggases in den geschlossenen Behälter und zum Veranlassen, dass das Sauggas in den Kompressionsabschnitt nach dem Kühlen des Motors gesaugt wird, vorgesehen ist,
    ein Auslassrohr (8), das zu dem geschlossenen Behälter zum Auslassen des Ansauggases, das von dem Kompressionsabschnitt komprimiert wurde, vorgesehen ist,
    eine Schmieröllagerkammer (4), die in dem geschlossenen Behälter (1) unterhalb des Kompressionsabschnitts (3) gebildet ist, und
    eine Ölversorgungspumpe (76), um ein Schmieröl (77) aus der Schmieröllagerkammer (4) zu saugen, die an einem unteren Ende der Hauptwelle (7) angeordnet ist,
    dadurch gekennzeichnet, dass
    der geschlossene Behälter (1) durch den Kompressionsabschnitt (3) in einen Motorgehäuseteil und die Schmieröllagerkammer (4) unterteilt ist, wobei das Saugrohr (5) an dem Motorgehäuseteil vorgesehen ist, wobei das Auslassrohr (8) an dem Kompressionsabschnitt (3) vorgesehen ist, und ein Ölversorgungsweg gebildet wird, wobei der Ölversorgungsweg von der Ölversorgungspumpe (76) in Verbindung steht, durch ein Inneres der Hauptwelle (7) läuft, sich an einem Hauptwellenlager (33B) der oberen stationären Spirale (33) öffnet, durch ein Hauptwellenlager der orbitierenden Spirale (31) durchgeht, durch ein Hauptwellenlager der unteren stationären Spirale (34) durchgeht und die Schmieröllagerkammer (4) erreicht.
  2. Scrollkompressor nach Anspruch 1, wobei
    eine Passage in dem Kompressionsabschnitt (3) zur Verbindung zwischen dem Motorgehäuseteil und der Schmieröllagerkammer (4) vorgesehen ist, und ein Rückschlagventil, um Rückstrom des Schmieröls vorzubeugen, an einer Öffnung des Durchgangs an der Schmieröllagerkammer vorgesehen ist.
  3. Scrollkompressor nach Anspruch 1, wobei eine Ansaugöffnung (33A) zur Verbindung zwischen dem Motorgehäuseteil und der Kompressionskammer (32) an einem äußeren umfänglichen Abschnitt der oberen stationären Spirale (33) des Kompressionsabschnitts vorgesehen ist.
  4. Scrollkompressor nach einem der Ansprüche 1 bis 3, wobei das Saugrohr (5) an dem geschlossenen Behälter (1) in einer Nähe des Kompressionsabschnitts (3) vorgesehen ist, und eine Glasanschlussklemme (6) an einem oberen Endabschnitt des geschlossenen Behälters vorgesehen ist.
  5. Scrollkompressor nach einem der Ansprüche 1 bis 4, wobei das Dichtmittel (31D) an der orbitierenden Spirale (31) zum Abdichten der Kompressionskammern (32), die zwischen der orbitierenden Spirale und den stationären Spiralen gebildet sind, von einem orbitierenden Lager (31D), das an der Hauptwellenseite der orbitierenden Spirale vorgesehen ist, und Hauptwellenlagern (33B/34C), die zwischen den stationären Spiralen und der Hauptwelle (7) vorgesehen sind, vorgesehen ist.
  6. Scrollkompressor nach Anspruch 5, wobei das Dichtmittel (31D) an einem Kernteil (31A) der orbitierenden Spirale (31) an deren Oberflächen, die zu den stationären Spiralen (33/34) gerichtet sind, vorgesehen ist.
  7. Scrollkompressor nach Anspruch 5 oder 6, wobei eine Auslassöffnung (34F) komprimierten Gases in einem Mittenabschnitt der stationären Spirale (34) an einer Stelle vorgesehen ist, die nicht über dem Dichtmittel (31D) liegt.
  8. Scrollkompressor nach Anspruch 7, wobei die Auslassöffnung (34F) nur an einer der stationären Spiralen (33/34) vorgesehen ist, und eine Verbindungsöffnung (31K) durch die orbitierende Grundplatte (31B) hindurch in der Nähe des Kernteils (31A) der orbitierenden Spirale (31) und außerhalb des Dichtmittels (31D) vorgesehen ist, und die Verbindungsöffnung (31K) nicht über den Kompressionskammern (32) liegt und immer mit der Auslassöffnung (34F) in Verbindung steht.
  9. Scrollkompressor nach Anspruch 8, wobei die Auslassöffnung (34F) und die Verbindungsöffnung (31K) jeweils als ein langes Loch oder durch eine Vielzahl von Löchern, die nebeneinanderliegen, gebildet sind.
EP04807594.9A 2004-12-22 2004-12-22 Kompressor der spiralbauart Expired - Fee Related EP1830067B1 (de)

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EP16176715.7A Division-Into EP3096017B1 (de) 2004-12-22 2004-12-22 Spiralverdichter

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US20090185936A1 (en) 2009-07-23
KR100811361B1 (ko) 2008-03-07
CN1938519A (zh) 2007-03-28
JPWO2006067843A1 (ja) 2008-06-12
EP3096017A1 (de) 2016-11-23
EP1830067A1 (de) 2007-09-05
WO2006067843A1 (ja) 2006-06-29
ES2817951T3 (es) 2021-04-08
EP1830067A4 (de) 2010-12-22
KR20070033958A (ko) 2007-03-27
US7614860B2 (en) 2009-11-10
US7909592B2 (en) 2011-03-22
CN100434702C (zh) 2008-11-19
EP3096017B1 (de) 2020-08-26
US20080219871A1 (en) 2008-09-11
JP4821612B2 (ja) 2011-11-24

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